JPH08169247A - Torque divider and drive train sub assembly - Google Patents

Torque divider and drive train sub assembly

Info

Publication number
JPH08169247A
JPH08169247A JP19101295A JP19101295A JPH08169247A JP H08169247 A JPH08169247 A JP H08169247A JP 19101295 A JP19101295 A JP 19101295A JP 19101295 A JP19101295 A JP 19101295A JP H08169247 A JPH08169247 A JP H08169247A
Authority
JP
Japan
Prior art keywords
shaft
output shaft
housing
torque
distribution device
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
JP19101295A
Other languages
Japanese (ja)
Inventor
David C Reuter
デイヴィド、シー、ロイタ
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Dana Inc
Original Assignee
Dana Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Dana Inc filed Critical Dana Inc
Publication of JPH08169247A publication Critical patent/JPH08169247A/en
Pending legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
    • B60K17/342—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a longitudinal, endless element, e.g. belt or chain, for transmitting drive to wheels
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/22—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or type of main drive shafting, e.g. cardan shaft
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
    • B60K17/344—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Arrangement And Driving Of Transmission Devices (AREA)

Abstract

PROBLEM TO BE SOLVED: To reduce costs by eliminating the necessity of a slide spline shaft associated with universal joints which are positioned outside a torque distribution device so as to be adapted to axial movement and angular movement between the front output shaft of the torque distribution device and the front drive shaft of a vehicle. SOLUTION: This torque distribution device 10 for a four-wheel drive vehicle having a housing 44, an input shaft 52, a sprocket shaft 76 and output shafts 54, 56 all of which are rotatably supported within the housing 44 further includes connection means 72, 74 for connecting the input shaft to the sprocket shaft in such a way as to provide driving action and a telescopic constant-velocity joint 80 which transfers torque from the sprocket shaft to the output shaft when inserted in the housing and connected to the sprocket shaft and the output shaft to rotate the sprocket shaft. The telescopic constant-velocity joint is further adapted in translation to the output shaft with respect to the sprocket shaft.

Description

【発明の詳細な説明】Detailed Description of the Invention

【０００１】[0001]

【産業上の利用分野】本発明は、一般に４輪駆動車用の
トルク分配装置（ｔｏｒｑｕｅ ｔｒａｎｓｆｅｒ ｃ
ａｓｅ）ことに車両の前部駆動軸に連結する傾斜した前
部出力軸を備えこの前部出力軸に伸縮式定速度自在継手
（ｔｅｌｅｓｃｏｐｉｎｇ ｃｏｎｓｔａｎｔ ｖｅｌ
ｏｃｉｔｙ ｕｎｉｖｅｒｓａｌ ｊｏｉｎｔ）を介し
てトルクを移送する４輪駆動トルク分配装置に関する。FIELD OF THE INVENTION The present invention generally relates to a torque transfer device for four-wheel drive vehicles.
In particular, an inclined front output shaft that is connected to the front drive shaft of the vehicle is provided, and the telescopic constant velocity joint is attached to the front output shaft.
The present invention relates to a four-wheel drive torque distribution device that transfers torque via an occupancy universal joint.

【０００２】[0002]

【発明の背景】車両用４輪駆動システムは、かなり利用
されていて車両に対し索引力が増大し運転の安全性が得
られる。従来このようなシステムは一般に、車両に対し
２輪又は４輪の駆動モデルを選択するように車両操縦者
が操作できる選択制御手段を設けた車両変速機の出力側
に結合したトルク分配装置を備えている。なお近年で
は、フル−タイム４輪駆動システム（“ｆｕｌｌ−ｔｉ
ｍｅ” ｆｏｕｒ−ｗｈｅｅｌ ｄｒｉｖｅ ｓｙｓｔ
ｅｍ）が車両に対し開発されている。この場合トルク分
配装置は典型的には、車両の前後の差動装置間にトルク
を分割する車軸間差動装置を設けてある。さらに前後輪
間の過度の滑りを防ぐように、公知の４輪駆動トルク分
配装置は典型的には、分配装置の前後の出力軸間の所定
の滑りを検知したときに車軸間差動装置を鎖錠するよう
に作動する選択係合クラッチを備えている。さらに公知
のトルク分配装置は、第２の出力軸に対し傾斜した第１
の出力軸を備え車両の前後の差動装置にトルクを有効に
移せるようにしてある。負荷状態の車両エンジンの運動
によって車両の前部車軸は、トルク分配装置に対して動
く。従来の４輪駆動システムでは、トルク分配装置及び
前部差動装置間のこの相対運動は典型的には、トルク分
配装置の前部出力軸を車両の前部枢動軸にねじり作用を
伴って連結するのに使う滑りスプライン継手によって適
応する。滑りスプライン継手は互いに組合う回転軸間の
軸線方向の相対運動に適応するのに有効であるが、これ
等の継手は、駆動軸又は推進軸と一体にすると製造費が
比較的高くなる。従って本発明以前には、継手角度（ｊ
ｏｉｎｔ ａｎｇｌｅ）を最小にし、組合う軸間の軸線
方向相対運動に適応するようにトルク分配装置の傾斜し
た前部出力軸を、車両前部枢動軸に協力させる費用的に
有効な手段を持つトルク分配装置が必要であった。BACKGROUND OF THE INVENTION Four-wheel drive systems for vehicles have been used extensively to increase the indexing force on the vehicle and provide driving safety. Conventionally, such systems typically include a torque distribution device coupled to the output side of the vehicle transmission which includes selection control means operable by the vehicle operator to select a two-wheel or four-wheel drive model for the vehicle. ing. In recent years, full-time four-wheel drive systems (“full-ti”
me ”four-wheel drive system
em) has been developed for vehicles. In this case, the torque distributor is typically provided with an inter-axle differential that splits the torque between the front and rear differentials of the vehicle. To further prevent excessive slip between the front and rear wheels, known four-wheel drive torque distributors typically engage an inter-axle differential when a predetermined slip between the front and rear output shafts of the distributor is detected. A selective engagement clutch is provided that operates to lock. A further known torque distribution device is a first torque device which is inclined with respect to a second output shaft.
The output shaft of is used to effectively transfer the torque to the front and rear differentials of the vehicle. The movement of the vehicle engine under load causes the front axle of the vehicle to move relative to the torque distributor. In conventional four-wheel drive systems, this relative movement between the torque distributor and the front differential typically involves twisting the front output shaft of the torque distributor to the front pivot shaft of the vehicle. Adapted by sliding spline joints used to connect. Although sliding spline joints are effective in accommodating axial relative motion between mating rotating shafts, these joints are relatively expensive to manufacture when integrated with a drive or propulsion shaft. Therefore, prior to the present invention, the joint angle (j
cost effective means for coordinating the inclined front output shaft of the torque distribution device with the vehicle front pivot shaft to minimize axial angle and accommodate axial relative movement between the mating shafts. A torque distributor was needed.

【０００３】[0003]

【発明の開示】従って本発明は、エンジン及び変速機ア
センブリからそれぞれ前後の差動装置に駆動作用を生ず
るように連結した前後の駆動軸にトルクを分配する、４
輪駆動車両用のトルク分配装置に係わる。本発明の好適
な実施例によれば、トルク分配装置は、入力軸及び駆動
スプロケット軸を回転できるように支えるハウジングを
備えている。トルク分配装置はさらに、入力軸をスプロ
ケット軸に駆動作用を生ずるように連結する手段と、ハ
ウジング内に入れられた伸縮式定速度（ＣＶ）継手とを
備えている。トルク分配装置はさらに、ハウジング内に
回転可能に支えられ、縦方向中心軸線を持つ出力軸を備
えている。伸縮式ＣＶ継手は、スプロケット軸及び出力
軸に結合され、スプロケット軸を回転するときに、スプ
ロケット軸から出力軸にトルクを移送しスプロケット軸
に対する出力軸の並進に適応するようにしてある。DISCLOSURE OF THE INVENTION Accordingly, the present invention distributes torque from the engine and transmission assembly to the front and rear drive shafts that are drivingly coupled to the front and rear differentials, respectively.
A torque distributor for a wheel drive vehicle. According to a preferred embodiment of the present invention, the torque distribution device comprises a housing for rotatably supporting the input shaft and the drive sprocket shaft. The torque distributor further comprises means for drivingly connecting the input shaft to the sprocket shaft and a telescopic constant velocity (CV) joint contained within the housing. The torque distributor further includes an output shaft rotatably supported within the housing and having a central longitudinal axis. The telescopic CV joint is connected to the sprocket shaft and the output shaft, and when rotating the sprocket shaft, it transfers torque from the sprocket shaft to the output shaft to accommodate translation of the output shaft with respect to the sprocket shaft.

【０００４】本発明のトルク分配装置の主な利点は、ハ
ウジング内に入れられた伸縮式ＣＶ継手を設け、この伸
縮式ＣＶ継手が、スプロケット軸に対する出力軸の並進
に適応する子とによって、トルク分配装置の前部出力軸
と車両の前部駆動軸との間の軸線方向運動及び角度的運
動に適応するように、トルク分配装置の外部にそれぞれ
位置させられる自在継手に関連する滑りスプライン軸
（ｓｌｉｐ ｓｐｌｉｎｅ ｓｈａｆｔ）の必要性を除
去することによって費用を節約することである。The main advantage of the torque distribution system of the present invention is that it provides a telescoping CV joint housed within a housing, the telescoping CV joint, with a child adapted to translate the output shaft relative to the sprocket shaft. A sliding spline shaft associated with a universal joint respectively positioned outside the torque distributor to accommodate axial and angular movement between the front output shaft of the distributor and the front drive shaft of the vehicle. Saving costs by eliminating the need for a slip spline shaft.

【０００５】本発明の前記した利点と共にその他の利点
は、添付図面についての好適な実施例の以下の詳細な説
明から明らかである。These and other advantages of the present invention will be apparent from the following detailed description of the preferred embodiment thereof, taken in conjunction with the accompanying drawings.

【０００６】[0006]

【実施例】図１及び２は本発明のトルク分配装置（ｔｏ
ｒｑｕｅ ｔｒａｎｓｆｅｒ ｃａｓｅ）１０を備えた
４輪駆動システムを示す。トルク分配装置１０は、車両
駆動エンジン１４に結合した普通の変速機ユニット１２
に結合してある。トルク分配装置１０は、普通の自在継
手２０により後部駆動軸１８の前端部に連結した後部出
力軸又は連結部材１６を備えている。後部駆動軸１８の
後端部は、自在継手２６により後部差動装置２４の入力
軸又はヨ−ク２２に結合してある。後部差動装置２４は
後部駆動軸１８からのトルクを車両の後車輪間に分割す
るようにしてある。1 and 2 show a torque distribution device (to of the present invention.
1 shows a four-wheel drive system with an rque transfer case) 10. The torque distribution device 10 includes a conventional transmission unit 12 coupled to a vehicle drive engine 14.
Is connected to. The torque distributor 10 includes a rear output shaft or connecting member 16 connected to the front end of a rear drive shaft 18 by a conventional universal joint 20. The rear end of the rear drive shaft 18 is connected by a universal joint 26 to the input shaft or yoke 22 of the rear differential 24. The rear differential 24 is adapted to split the torque from the rear drive shaft 18 between the rear wheels of the vehicle.

【０００７】トルク分配装置１０は又、自在継手３４に
より車両の前部駆動軸３２の前端部に駆動作用を生ずる
ように連結した前部出力軸又は連結部材３０を設けてあ
る。前部駆動軸３２は、自在継手４０により車両の前部
差動装置３８の入力軸又はヨ−ク３６に前端部を連結し
てある。前部差動装置３８は前部駆動軸３２から受ける
トルクを分割するようにしてある。The torque distributor 10 also includes a front output shaft or connecting member 30 that is operatively connected to the front end of a vehicle front drive shaft 32 by a universal joint 34. The front drive shaft 32 is connected at its front end by a universal joint 40 to an input shaft or yoke 36 of a front differential 38 of the vehicle. The front differential 38 is adapted to split the torque received from the front drive shaft 32.

【０００８】後部駆動軸１８は、縦方向中心軸線４３の
まわりに回転し、又前部駆動軸３２は軸線４５のまわり
に回転する。図２に明らかなように本発明の好適な実施
例では後部駆動軸１８は、トルク分配装置１０から後部
差動装置２４の方に下方に傾斜し、又前部駆動軸３２は
トルク分配装置１０から前部差動装置３８の方に下方に
傾斜している。トルク分配装置１０の後部出力軸１６と
後部差動装置２４の入力軸２２とは、実質的にまっすぐ
な線に軸線４３に沿い直列の関係に配置され、すなわち
軸１６、１８、２２の縦方向軸線がそれぞれ軸線４３に
一致し、そして各軸は相互に直列の関係に配置してあ
る。同様にトルク分配装置１０の前部出力軸３０と、前
部駆動軸３２と、前部差動装置３８の入力軸３６とは実
質的にまっすぐな線に軸線４５に沿い直列の関係に配置
するのがよい。しかし若干の車両用では、前後部の直線
関係のいずれか又は両方を達成することはできない。こ
れ等の例では、さらに１９８９年８月２９日付米国特許
第４，８６０，６１２号明細書「４輪駆動システム用車
両トルク分配装置（Ｖｅｈｉｃｌｅ ＴｏｒｑｕｅＴｒ
ａｎｓｆｅｒ Ｃａｓｅ ｆｏｒ ａ Ｆｏｕｒ−Ｗｈ
ｅｅｌ ＤｒｉｖｅＳｙｓｔｅｍ）」に記載してあるよ
うに付加的な駆動構造を使うことができる。この特許明
細書は本説明に参照してある。The rear drive shaft 18 rotates about a longitudinal centerline axis 43 and the front drive shaft 32 rotates about an axis 45. As is apparent from FIG. 2, in the preferred embodiment of the present invention, the rear drive shaft 18 tilts downwardly from the torque distributor 10 toward the rear differential 24, and the front drive shaft 32 includes the torque distributor 10. Tilts downwards from the front towards the front differential 38. The rear output shaft 16 of the torque distributor 10 and the input shaft 22 of the rear differential 24 are arranged in series relationship along the axis 43 in a substantially straight line, i.e. in the longitudinal direction of the shafts 16, 18, 22. The axes each correspond to the axis 43, and the axes are arranged in series with one another. Similarly, the front output shaft 30, the front drive shaft 32, and the input shaft 36 of the front differential 38 of the torque distributor 10 are arranged in a substantially straight line in series relationship along the axis 45. Is good. However, for some vehicles, either or both of the front and rear linear relationships cannot be achieved. In these examples, further, U.S. Pat. No. 4,860,612 of Aug. 29, 1989, "Vehicle TorqueTr for a four-wheel drive system (Vehicle TorqueTr).
Transfer Case for a Four-Wh
Additional drive structures can be used as described in "Eel Drive System". This patent is referred to in this description.

【０００９】さらに好適な実施例では軸線４３、４５
は、互いに間隔を置いて上下方向に向いた実質的に互い
に平行な平面に位置している。従ってこの駆動構造を達
成するには、トルク分配装置１０の前部出力軸３０は、
図２に示すようにトルク分配装置１０の後部出力軸１６
から横方向に間隔を置いて後部出力軸１６に対して傾斜
しなければならない。従って軸線４５の延長部分である
前部出力軸３０の軸線は、軸線４３の延長部分である後
部出力軸１６に平行でなく又交差しなくて、軸１６、３
２の軸線は食違い線を形成する。引続いて述べるように
トルク分配装置１０の傾斜出力軸構造は伸縮式定速度自
在継手を使って得られる。In a more preferred embodiment, the axes 43, 45
Are located in planes which are spaced apart from each other and which face in the vertical direction and are substantially parallel to each other. Therefore, in order to achieve this drive structure, the front output shaft 30 of the torque distribution device 10 is
As shown in FIG. 2, the rear output shaft 16 of the torque distribution device 10
Must be inclined laterally at a distance relative to the rear output shaft 16. Therefore, the axis of the front output shaft 30, which is an extension of the axis 45, is neither parallel nor intersects with the rear output shaft 16, which is an extension of the axis 43, and the axes 16, 3,
The two axes form a staggered line. As will be described subsequently, the tilted output shaft structure of the torque distribution device 10 is obtained by using a telescopic constant velocity universal joint.

【００１０】図３及び４に示すように本発明のトルク分
配装置１０の好適な実施例の特定の構造を以下に詳細に
述べる。トルク分配装置１０は、複数本のボルト（図示
していない）及び位置決めピン５０のような普通の手段
により相互に締付けた前部部分４６及び後部部分４８を
持つ割りハウジング４４を備えている。トルク分配装置
１０はさらに、ハウジング４４内に回転できるように支
えられた入力軸５２を備えている。この場合入力軸５２
は、スプライン連結部５５を介して車両変速機１２（図
１及び２に示してある）の出力軸５３に駆動作用を伴っ
て連結してある。トルク分配装置１０は又、ハウジング
４４内に回転できるように支えられ車両の後部駆動軸１
８（図１及び２に示してある）に連結するようにした後
部出力軸５４と、車両の前部駆動軸３２に連結するよう
にした前部出力軸５６とを備えている。トルク分配装置
１０はさらに、後部出力軸５４及び前部出力軸５６間に
トルクを分割する車軸間遊星歯車差動装置５８を備えて
いる。The specific construction of the preferred embodiment of the torque distribution device 10 of the present invention as shown in FIGS. 3 and 4 is described in detail below. The torque distributor 10 comprises a split housing 44 having a front portion 46 and a rear portion 48 which are clamped together by conventional means such as a plurality of bolts (not shown) and locating pins 50. The torque distribution device 10 further includes an input shaft 52 rotatably supported within the housing 44. In this case the input shaft 52
Is connected to the output shaft 53 of the vehicle transmission 12 (shown in FIGS. 1 and 2) via a spline connection 55 with driving action. The torque distribution device 10 is also rotatably supported within the housing 44 and is a rear drive shaft 1 of the vehicle.
8 (shown in FIGS. 1 and 2) and a front output shaft 54 adapted to be connected to the front drive shaft 32 of the vehicle. The torque distribution device 10 further includes an inter-axle planetary gear differential 58 that divides the torque between the rear output shaft 54 and the front output shaft 56.

【００１１】入力軸５２はその後端部を遊星歯車差動装
置５８の遊星歯車受け（ｐｌａｎｅｔ ｃａｒｒｉｅ
ｒ）６２に固定する。この場合遊星歯車受け６２は円周
方向に互いに間隔を置いて個別に回転できる複数個の遊
星歯車６４を支える。管状軸部材６６は、入力軸５２の
まわりに回転できるように取付けられその後端部の遊星
太陽歯車６８と前端部の駆動スプロケット７０とを備え
ている。各遊星歯車６４は遊星歯車差動装置５８の遊星
太陽歯車６８及び遊星リングギヤ８２にかみある。駆動
スプロケット７０は、スプライン７１を介し管状軸６６
にスプライン連結され駆動チェ−ン７２に連結してあ
る。駆動チェ−ン７２は、スプライン７８によりスプロ
ケット軸７６に駆動作用を生ずるように連結した第２の
駆動スプロケット７４を駆動する。なお詳しく述べるよ
うに伸縮式定速度（ＣＶ）継手８０は、トルク分配装置
１０のハウジング４４内に入れられ、スプロケット軸７
６及び傾斜前部出力軸５６に結合され、スプロケット軸
７６を回転するときにスプロケット軸７６から前部出力
軸５６にトルクを移送する。遊星リングギヤ８２に取付
けられ、スプライン８６により後部出力軸５４にスプラ
イン結合された（ｓｐｌｉｎｅｄ）リンクギヤ（ｌｉｎ
ｋ ｇｅａｒ）８４により、遊星リングギヤ８２は、後
部出力軸５４に駆動作用を生ずるように連結されてい
る。後部出力軸５４は、前端部を軸受アセンブリ８８に
より又中央部分を軸受アセンブリ８９によりハウジング
４４内に回転できるように支えてある。管状の軸部材６
６は軸受アセンブリ９２、９４によりハウジング４４内
に支えてある。入力軸５２は軸受アセンブリ９５及びジ
ャ−ナル軸受９６によりスリ−ブ部材すなわち管状軸部
材６６に回転できるように支えてある。The input shaft 52 has at its rear end a planetary carrier of a planetary gear differential 58.
r) Fix to 62. In this case, the planetary gear receiver 62 supports a plurality of planetary gears 64 that are spaced apart from one another in the circumferential direction and can rotate individually. The tubular shaft member 66 is rotatably mounted about the input shaft 52 and includes a planet sun gear 68 at its rear end and a drive sprocket 70 at its front end. Each planet gear 64 meshes with the planet sun gear 68 and the planet ring gear 82 of the planet gear differential 58. The drive sprocket 70 has a tubular shaft 66 through a spline 71.
Is splined to the drive chain 72. The drive chain 72 drives a second drive sprocket 74 that is drivingly connected to the sprocket shaft 76 by a spline 78. As will be described in more detail, the telescopic constant velocity (CV) joint 80 is housed in the housing 44 of the torque distribution device 10 and the sprocket shaft 7
6 and the tilted front output shaft 56, transfer torque from the sprocket shaft 76 to the front output shaft 56 as the sprocket shaft 76 rotates. A link gear (lin) mounted on the planet ring gear 82 and splined to the rear output shaft 54 by a spline 86.
The planetary ring gear 82 is operatively connected to the rear output shaft 54 by a k gear 84. The rear output shaft 54 is rotatably supported within the housing 44 by a bearing assembly 88 at a front end and a bearing assembly 89 at a central portion. Tubular shaft member 6
6 is supported within the housing 44 by bearing assemblies 92,94. The input shaft 52 is rotatably supported by a sleeve member or tubular shaft member 66 by a bearing assembly 95 and a journal bearing 96.

【００１２】遊星歯車差動装置５８を選択的に鎖錠する
電磁クラッチ・アセンブリ６０は、遊星リングギヤ８２
に一緒に回転するように固着する第１群のクラッチ板
と、太陽歯車６８と一緒に回転するように軸部材６６に
固着する第２群のクラッチ板とを備えている。第１及び
第２の群のクラッチ板の各別の板は相互に軸線方向に交
互の関係に配置してある。同軸のクラッチコイル９８は
クラッチ板に隣接して位置し電子制御システム（図示し
てない）からクラッチ係合信号を受ける。この電子制御
システムは、後部出力軸５４及び前部出力軸５６の速度
を計測する速度センサ（図示してない）から入力信号を
受ける。前記したように遊星歯車差動装置５８は、後部
出力軸５４及び前部出力軸５６間にトルクを分割するよ
うに設けてある。車両の若干の運転条件中に出力軸５
４、５６間に所定の滑りにより、車両の旋回時のように
正常な牽引条件中に生ずる互いにわずかに異なる前後輪
速度に適応できることが望ましい。しかし出力軸５４、
５６間の滑りが所定量に達すると、出力軸５４、５６間
にもはや相対滑りが生じないようにすることが望まし
い。このことは、前記した米国特許第４，８６０，６１
２号明細書と本願に参照した１９９２年５月２６日付米
国特許第５，１１６，２９３号明細書とになお詳しく記
載してあるように、後部出力軸５４及び前部出力軸５６
の監視速度に基づいて電子制御装置からの信号によりク
ラッチコイル９８に通電することによってできる。クラ
ッチコイル９８に通電するときは、第１及び第２の群の
クラッチ板は互いに押圧され相互に摩擦を伴って係合し
太陽歯車６８及びリングギヤ８２が相互に鎖錠するよう
になる。この状態が生ずると、入力軸５２と前部出力軸
５６及び後部出力軸５４との間に直接駆動の連結状態が
生ずる。このようにして、クラッチコイル９８に通電し
ている時間中に、低摩擦係数の表面との接触によって滑
動する車輪を駆動する車軸に対向する車両車軸に協働す
る分配装置出力軸に付加的なトルクを伝えることができ
る。The electromagnetic clutch assembly 60 that selectively locks the planetary gear differential 58 includes a planetary ring gear 82.
And a second group of clutch plates that are fixedly attached to the shaft member 66 so as to rotate together with the sun gear 68. The separate plates of the first and second groups of clutch plates are arranged axially in alternating relation to each other. A coaxial clutch coil 98 is located adjacent the clutch plate and receives a clutch engagement signal from an electronic control system (not shown). The electronic control system receives input signals from a speed sensor (not shown) that measures the speed of the rear output shaft 54 and the front output shaft 56. As described above, the planetary gear differential device 58 is provided so as to divide the torque between the rear output shaft 54 and the front output shaft 56. Output shaft 5 during some driving conditions of the vehicle
It is desirable to be able to accommodate the slightly different front and rear wheel speeds that occur during normal traction conditions, such as when the vehicle is turning, due to the predetermined slippage between points 4 and 56. However, the output shaft 54,
When the slip between 56 reaches a certain amount, it is desirable to prevent relative slip between the output shafts 54, 56. This is the same as the above-mentioned US Pat. No. 4,860,61.
No. 2, and U.S. Pat. No. 5,116,293, dated May 26, 1992, which is incorporated herein by reference, as further described in detail in rear output shaft 54 and front output shaft 56.
It is possible to energize the clutch coil 98 by a signal from the electronic control unit based on the monitoring speed of the above. When the clutch coil 98 is energized, the clutch plates of the first and second groups are pressed against each other and frictionally engage each other, so that the sun gear 68 and the ring gear 82 lock each other. When this occurs, a direct drive connection occurs between the input shaft 52 and the front output shaft 56 and the rear output shaft 54. Thus, during the time that the clutch coil 98 is energized, an additional distributor output shaft that cooperates with the vehicle axle opposite the axle that drives the wheel that slides due to contact with the low coefficient of friction surface is added. Can transmit torque.

【００１３】駆動列サブアセンブリを備えたトルク分配
装置１０のスプロケット軸７６、伸縮式ＣＶ接手８０及
び傾斜した前部出力軸５６の間の相互関係は図４に一層
詳しく例示してある。駆動チェ−ン７２は、スプライン
７８を介しスプロケット７４にスプライン結合されたス
プロケット軸７６とスプロケット７４とを駆動する、ス
プロケット７４のスプロケット歯１００に掛けてある。
チェ−ン７２を駆動する、１変型としてスプロケット軸
７６は、スプロケット歯１００の代りに歯車歯が使われ
チェ−ン７２の代りに歯車を使う歯車列により駆動する
ことができる。スプロケット軸７６は、軸受アセンブリ
１０２、１０４によりハウジング４４内に回転できるよ
うに支えてある。The interrelationship between the sprocket shaft 76, the telescopic CV joint 80 and the beveled front output shaft 56 of the torque distributor 10 with the drive train subassembly is illustrated in more detail in FIG. The drive chain 72 is hung on the sprocket teeth 100 of the sprocket 74, which drives the sprocket 74 and the sprocket shaft 76 that is splined to the sprocket 74 via splines 78.
As a variant, the sprocket shaft 76, which drives the chains 72, can be driven by a gear train in which gear teeth are used instead of the sprocket teeth 100 and gears are used instead of the chains 72. Sprocket shaft 76 is rotatably supported within housing 44 by bearing assemblies 102, 104.

【００１４】伸縮式ＣＶ継手８０は、トルク分配装置の
ハウジング４４の端部キャップ１０６内に入れてある。
端部キャップ１０６は、ボルト１０８のような普通の手
段によりハウジング４４の前部分４６に締付けてある。
伸縮式ＣＶ継手８０は、スプライン１１２によりスプロ
ケット軸７６の前端部にスプライン結合された内レ−ス
１１０と、前部出力軸５６の拡大した中空端部１１６内
に一体に形成した外レ−ス１１４とを備えている。円周
方向に互いに間隔を置いたトルク伝達ボ−ル１１８（１
個だけ示してある）は、内レ−ス１１０及び外レ−ス１
１４の間に配置される。各トルク伝達ボ−ル１１８は、
外レ−ス１１４に形成した複数のみぞ１２０の１つと、
内レース１１０に形成した複数のみぞ１２１のうちの協
働し対応する１つとの中に受入れられる。トルク伝達ボ
−ル１１８は、外レ−ス１１４内のみぞ１２０と、内レ
−ス１１０内の対応するみぞ１２１との中にケ−ジ部材
１２２により保持されている。外レ−ス１１４内の各み
ぞ１２０は、前部出力軸５６の縦方向中心軸線１２４に
ほぼ平行な方向に縦方向に延びている。内レ−ス１１０
の各みぞ１２１は、スプロケット軸７６の縦方向中心軸
線１２５にほぼ平行な方向に縦方向に延びている。外レ
−ス１１４及び内レ−ス１１０の協働する縦方向にまっ
すぐなみぞ内のトルク伝達ボ−ル１１８の配置により、
出力軸５６を中心軸線１２４にほぼ平行な方向にスプロ
ケット軸７６に対し縦方向に並進させる。図４に例示し
た好適とする伸縮式定速度継手８０は二重オフセット伸
縮式定速度継手（ｄｏｕｂｌｅ ｏｆｆｓｅｔ ｔｅｌ
ｅｓｃｏｐｉｎｇ ｃｏｎｓｔａｎｔ ｖｅｌｏｃｉｔ
ｙ ｊｏｉｎｔ）であるが、任意の機能的に同等の定速
度継手を使ってもよいのは明らかである。交差みぞ形又
はトリポット型伸縮式継手（ｔｒｉｐｏｔ ｔｙｐｅ
ｔｅｌｅｓｃｏｐｉｎｇ ｊｏｉｎｔ）のような若干の
他の公知の形式の伸縮式定速度継手は、出力軸５６及び
スプロケット軸７６が相対的に傾斜することによってこ
のような継手の内レ−ス及び外レ−スの中心線が相対的
に半径方向に動くから、本発明の範囲内では使用できな
い。内レ−ス及び外レ−ス間のこの相対運動により継手
は固着し出力軸５６が必要に応じスプロケット軸７６に
対し縦方向に並進しないようにする。The telescopic CV coupling 80 is contained within the end cap 106 of the torque distributor housing 44.
The end cap 106 is fastened to the front portion 46 of the housing 44 by conventional means such as bolts 108.
The telescopic CV joint 80 includes an inner race 110 splined to a front end of a sprocket shaft 76 by a spline 112 and an outer race integrally formed in an enlarged hollow end 116 of the front output shaft 56. And 114. Torque transmission balls 118 (1
(Only one is shown) is an inner race 110 and an outer race 1
It is arranged between 14. Each torque transmission ball 118 is
One of a plurality of grooves 120 formed on the outer race 114,
It is received in a cooperating and corresponding one of a plurality of grooves 121 formed in the inner race 110. The torque transmission ball 118 is retained by a cage member 122 in a groove 120 in the outer race 114 and a corresponding groove 121 in the inner race 110. Each groove 120 in the outer race 114 extends longitudinally in a direction substantially parallel to the longitudinal central axis 124 of the front output shaft 56. Inner Race 110
Each groove 121 extends in the vertical direction in a direction substantially parallel to the central axis 125 in the vertical direction of the sprocket shaft 76. Due to the arrangement of the torque transmitting ball 118 in the cooperating longitudinal straight groove of the outer race 114 and the inner race 110,
The output shaft 56 is longitudinally translated with respect to the sprocket shaft 76 in a direction substantially parallel to the central axis 124. A preferred expansion constant velocity joint 80 illustrated in FIG. 4 is a double offset expansion constant velocity joint.
escoping constant velocity
However, it is clear that any functionally equivalent constant velocity joint may be used. Cross groove or tripod type expansion joint (tripot type)
Some other known types of telescoping constant velocity joints, such as telescoping joints, have inner and outer races of such joints due to the relative tilting of the output shaft 56 and the sprocket shaft 76. It cannot be used within the scope of the present invention because the centerline of R moves radially. This relative movement between the inner and outer races secures the joint and prevents the output shaft 56 from translating longitudinally with respect to the sprocket shaft 76, if desired.

【００１５】トルク分配装置１０はさらに、スプロケッ
ト軸７６を貫いて縦方向に延びる少なくとも１条の通路
１２６を持ち伸縮式ＣＶ継手８０を潤滑する手段を備え
ている。通路１２６は、スプロケット軸７５６の被駆動
端部１３２の近くに配置した空洞１３０に連通する第１
端部１２８を持つ。通路１２６の第２端部１３４は、伸
縮式ＣＶ継手８０内に位置する第２空洞１３６に連通す
る。好適とする実施例では通路１２６は、形状が一般に
円筒形で直径Ｄ１を持つが、本発明の範囲内で他の形状
の通路１２６を使ってもよい。空洞１３６は、直径Ｄ２
を持つ一般に円筒形の部分１３７を備え、部分１３７は
外レ−ス１１４の内面に対応する。空洞１３６の直径Ｄ
２は通路１２６の直径Ｄ１より大きくて、スプロケット
軸７６を回転するときに空洞１３６及び通路１２６の間
に差動圧力が生ずる。空洞１３６の容積はみぞ１２０の
容積により補助され空洞１３６及び通路１２６への間の
差動圧力をさらに増す。空洞１３６内の圧力は通路１２
６内の圧力より低く、伸縮式ＣＶ継手８０を潤滑するた
めに矢印１３８を示すように潤滑流体を空洞１３０から
通路１２６を経て空洞１３６に流す。The torque distributor 10 further includes means for lubricating the telescoping CV joint 80 having at least one passage 126 extending longitudinally through the sprocket shaft 76. The passage 126 communicates with a first cavity 130 located near the driven end 132 of the sprocket shaft 756.
It has an end 128. The second end 134 of the passage 126 communicates with a second cavity 136 located within the telescoping CV joint 80. In the preferred embodiment, the passages 126 are generally cylindrical in shape and have a diameter D1, but other shapes of passages 126 may be used within the scope of the present invention. The cavity 136 has a diameter D2
With a generally cylindrical portion 137 having a portion 137 corresponding to the inner surface of the outer race 114. Diameter D of cavity 136
2 is larger than the diameter D1 of the passage 126, and a differential pressure is generated between the cavity 136 and the passage 126 when rotating the sprocket shaft 76. The volume of cavity 136 is assisted by the volume of groove 120 to further increase the differential pressure between cavity 136 and passageway 126. The pressure in the cavity 136 is the passage 12
Below the pressure in 6, the lubricating fluid flows from cavity 130 through passage 126 into cavity 136 as indicated by arrow 138 to lubricate telescopic CV joint 80.

【００１６】トルク分配装置１０の連結部材３０は、傾
斜した前部出力軸５６の細くした部分１４２に対し囲む
関係に配置されスプライン１４４により細い部分１４２
にスプラインばめしてある。従って連結部材３０は、前
部出力軸５６と共に回転する。さらに前部出力軸５６に
対する連結部材３０の軸線方向変位を防ぐ手段を設けて
ある。この手段は、前部出力軸５６の前端部１４６にね
じ込んだナット１４５とワッシヤ１４８とから成ってい
る。この手段ではナット１４５及びワッシヤ１４８の組
合わせにより連結部材３０を前部出力軸５６の拡大した
中空端部１１６に対し付勢する。The connecting member 30 of the torque distributor 10 is disposed in a surrounding relationship with the tapered portion 142 of the inclined front output shaft 56 and is enclosed by the spline 144 in a thinner portion 142.
It is fitted with a spline. Therefore, the connecting member 30 rotates together with the front output shaft 56. Further, means for preventing axial displacement of the connecting member 30 with respect to the front output shaft 56 is provided. This means consists of a nut 145 and a washer 148 screwed into the front end 146 of the front output shaft 56. By this means, the combination of the nut 145 and the washer 148 biases the connecting member 30 against the enlarged hollow end 116 of the front output shaft 56.

【００１７】シ−ル・アセンブリ１５０は、ハウジング
４４の端部キャップ１０６に取付けられ、連結部材３０
対しそれぞれ囲む関係に配置した遮蔽１５４及び唇状シ
−ル１５８から成っている。唇状シ−ル１５８は、支持
部材１５２を介しハウジング４４の端部キャップ１０６
に取付けられ、ばね部材１５６により連結部材３０に対
し弾性的に付勢され分配装置１０のハウジング４４内に
円滑流体を保持するようにしてある。遮蔽１５４は、唇
状シ−ル１５８に向かって延び、唇状シ−ル１５８内へ
の汚れ及びその他の異物の侵入を防ぐのに使う。The seal assembly 150 is attached to the end cap 106 of the housing 44 and includes the connecting member 30.
It comprises a shield 154 and a lip seal 158 which are arranged in respective surrounding relations. The lip seal 158 is attached to the end cap 106 of the housing 44 via the support member 152.
And is elastically urged against the connecting member 30 by a spring member 156 to retain a smooth fluid in the housing 44 of the distributor 10. The shield 154 extends toward the lip seal 158 and is used to prevent dirt and other foreign matter from entering the lip seal 158.

【００１８】連結部材３０は、ブッシング１６０により
ハウジング４４の端部キャップ１０６内に回転できるよ
うに支えてある。ブッシング１６０は又、連結部材３０
及び前部出力軸５６を中心線１２４のまわりに心合せす
る。前部出力軸５６は、伸縮式ＣＶ継手８０の外レ−ス
１１４、内レ−ス１１０及びトルク伝達ボ−ル１１８に
よりハウジング４４内に回転できるように支えられ、又
細くした直径部分１４２と共に連結部材３０で回転でき
るように支えてある。図示の例に比べて軸５６の異なる
角度方向の向きに適応するのに他の端部キャップを使っ
てもよいのは明らかである。図示の実施例では、前出力
軸５６は、中心軸線１２４にほぼ平行な方向に約０．８
０ｉｎ（２．０３ｃｍ）の公称距離だけ並進し、４輪駆
動車両用のトルク分配装置の好適な実施例に対応する
０．２０ｉｎ（０．５０８ｃｍ）程度の範囲で並進する
のがよい。前部出力軸５６の他の範囲の並進も用途に従
って伸縮式ＣＶ継手８０の寸法を定めることにより適合
できる。The connecting member 30 is rotatably supported within the end cap 106 of the housing 44 by a bushing 160. The bushing 160 also includes the connecting member 30.
And center the front output shaft 56 about the centerline 124. The front output shaft 56 is rotatably supported within the housing 44 by the outer race 114, the inner race 110 and the torque transmission ball 118 of the telescoping CV joint 80, and together with the tapered diameter portion 142. It is rotatably supported by the connecting member 30. It will be appreciated that other end caps may be used to accommodate different angular orientations of shaft 56 as compared to the illustrated example. In the illustrated embodiment, the front output shaft 56 is approximately 0.8 in a direction generally parallel to the central axis 124.
It is preferable to translate by a nominal distance of 0 in (2.03 cm) and in the range of about 0.20 in (0.508 cm), which corresponds to the preferred embodiment of the torque distribution device for a four-wheel drive vehicle. Other ranges of translation of the front output shaft 56 can be accommodated by sizing the telescopic CV joint 80 according to the application.

【００１９】連結部材３０は、前部出力軸５６を車両の
前部駆動軸３２に駆動作用を生ずるように連結するため
に前部駆動軸３２に取付ける普通の自在継手又はカルダ
ン継手にボルト締めする。図３及び４に示した好適な実
施例では連結部材３０はフランジ形連結部材でよいが、
或いは普通の自在継手に連結したヨ−クを備えてもよ
い。ハウジング４４内に納めた伸縮式ＣＶ継手８０の使
用より、前部駆動軸３２内のように共にハウジング４４
外に位置させた滑りスプライン軸及び自在継手の比較的
高価な組合わせの必要がなくなる。さらに伸縮式ＣＶ継
手８０をシ−ル・アセンブリ１５０によりハウジング４
４内に保持した潤滑流体内に浸すことによって、普通の
ゴムブ−ツ内に納められ普通の条件にさらされるグリ−
ス詰めの自在継手に対しＣＶ継手８０の寿命を延ばす。
さらに本発明の構成により、後部出力軸５４と協働して
図３に示した輸送キャップ１４９（連結部材１６の代り
に）と同様に構成したハウジング４４内に潤滑流体を保
持するのに前部出力軸５６を囲む輸送キャップの必要が
なくなる。The connecting member 30 is bolted to a conventional universal joint or cardan joint which is mounted to the front drive shaft 32 for drivingly connecting the front output shaft 56 to the front drive shaft 32 of the vehicle. . In the preferred embodiment shown in FIGS. 3 and 4, the connecting member 30 may be a flange type connecting member,
Alternatively, it may be provided with a yoke connected to an ordinary universal joint. Due to the use of the telescopic CV joint 80 housed in the housing 44, the housing 44 is housed together as in the front drive shaft 32.
Eliminates the need for a relatively expensive combination of externally located sliding spline shaft and universal joint. Further, the telescopic CV joint 80 is attached to the housing 4 by the seal assembly 150.
A grease that is stored in a normal rubber boot and is exposed to normal conditions by immersing it in a lubricating fluid held in 4.
Extends the life of the CV joint 80 compared to the space-filled universal joint.
Further, in accordance with the inventive arrangements, a front portion for retaining a lubricating fluid in a housing 44 configured in cooperation with the rear output shaft 54 and configured similarly to the transport cap 149 (instead of the connecting member 16) shown in FIG. The need for a shipping cap surrounding the output shaft 56 is eliminated.

【００２０】以上本発明の好適とする実施例について詳
細に説明したが、本発明はその精神を逸脱しないでなお
種種の変化変型を行うことができるのはもちろんであ
る。たとえばトルク分配装置は、傾斜前部出力軸でなく
て傾斜後部出力軸と協働して本発明の伸縮式ＣＶ継手を
利用するのが有利であり、又は後部及び前部の出力軸と
協働して利用してもよい。さらに車両変速機と前後部の
差動装置とのような他の駆動列サブアセンブリは、本発
明の伸縮式ＣＶ継手を利用するのが有利である。この伸
縮式ＣＶ継手は前部又は後部の差動装置に対し変速機出
力軸又は入力軸と協働して使えばよい。従って本発明は
前記した特定の実施例だけに限定するものではない。Although the preferred embodiments of the present invention have been described in detail above, it is needless to say that the present invention can be modified in various ways without departing from the spirit thereof. For example, the torque distributor may advantageously utilize the telescoping CV joint of the present invention in cooperation with a tilted rear output shaft rather than a tilted front output shaft, or with rear and front output shafts. You may use it. Still other drivetrain subassemblies, such as vehicle transmissions and front and rear differentials, advantageously utilize the telescoping CV joints of the present invention. This telescopic CV joint may be used in conjunction with a transmission output shaft or input shaft for a front or rear differential. Therefore, the present invention is not limited to the particular embodiments described above.

【図面の簡単な説明】[Brief description of drawings]

【図１】本発明トルク分配装置を協働させた車両４輪駆
動システムの平面図である。FIG. 1 is a plan view of a vehicle four-wheel drive system that cooperates with a torque distribution device of the present invention.

【図２】本発明分配装置の傾斜した前部出力軸を示す図
１の側面図である。2 is a side view of FIG. 1 showing a tilted front output shaft of the dispensing device of the present invention.

【図３】本発明のトルク分配装置の縦断面図である。FIG. 3 is a vertical cross-sectional view of the torque distribution device of the present invention.

【図４】本発明のトルク分配装置の伸縮式ＣＶ継手及び
傾斜した前部出力軸を拡大して示す部分縦断面図であ
る。FIG. 4 is a partial vertical cross-sectional view showing an expandable CV joint and a tilted front output shaft of the torque distribution device of the present invention in an enlarged manner.

【符号の説明】[Explanation of symbols]

１０ トルク分配装置 ４４ ハウジング ５２ 入力軸 ５４、５６ 出力軸 ７６ スプロケット軸 ８０ 伸縮式定速度継手 10 Torque distributor 44 Housing 52 Input shaft 54, 56 Output shaft 76 Sprocket shaft 80 Telescopic constant velocity joint

─────────────────────────────────────────────────────
─────────────────────────────────────────────────── ───

【手続補正書】[Procedure amendment]

【提出日】平成７年１０月５日[Submission date] October 5, 1995

【手続補正１】[Procedure Amendment 1]

【補正対象書類名】明細書[Document name to be amended] Statement

【補正対象項目名】特許請求の範囲[Name of item to be amended] Claims

【補正方法】変更[Correction method] Change

【補正内容】[Correction content]

【特許請求の範囲】[Claims]

Claims (15)

【特許請求の範囲】[Claims] 【請求項１】 ハウジングと、 このハウジング内に回転可能に支えられた入力軸と、 前記ハウジング内に回転可能に支えられたスプロケット
軸と、 前記入力軸を前記スプロケット軸に駆動作用が生ずるよ
うに連結する連結手段と、 前記ハウジング内に入れられた伸縮式定速度継手と、 縦方向中心軸線を持ち、前記ハウジング内に回転可能に
支えられた出力軸と、を備え、 前記スプロケット軸を回転するときに、このスプロット
軸から前記出力軸にトルクを移送するように、前記伸縮
式定速度継手を、前記スプロット軸及び出力軸に結合
し、 前記伸縮式定速度継手が、前記スプロット軸に対する前
記出力軸の並進に適応するようにして成るトルク分配装
置。1. A housing, an input shaft rotatably supported in the housing, a sprocket shaft rotatably supported in the housing, and a driving action for the input shaft to the sprocket shaft. Rotating the sprocket shaft, which comprises a connecting means for connecting, an expansion-type constant velocity joint housed in the housing, and an output shaft having a longitudinal center axis and rotatably supported in the housing. At this time, the telescopic constant velocity joint is coupled to the splot shaft and the output shaft so that torque is transferred from the splot shaft to the output shaft, and the telescopic constant velocity joint outputs the output to the splot shaft. A torque distribution device adapted to accommodate axial translation. 【請求項２】 前記伸縮式定速度継手に、内レースと、
外レースと、これ等の内レースと外レースとの間に配置
された少なくとも１個のトルク伝達ボールとを設け、 前記内レースを、前記スプロット軸の一端部にスプライ
ン結合し、 前記外レースを、前記出力軸の拡大した中空端部内に一
体に形式して成る、請求項１のトルク分配装置。2. The expansion type constant velocity joint, an inner race,
An outer race and at least one torque transmission ball arranged between the inner race and the outer race are provided, and the inner race is spline-coupled to one end of the sprout shaft to form the outer race. The torque distribution device of claim 1, wherein the torque distribution device is integrally formed within the enlarged hollow end of the output shaft. 【請求項３】 前記の少なくとも１個のトルク伝達ボー
ルを、前記外レースに形成された第１のみぞと、前記内
レースに形成された第２のみぞとの中に受入れ、 前記少なくとも１個のトルク伝達ボールが、前記外レー
スの第１みぞと、前記内レースの第２みぞとに協働し
て、前記出力軸前記縦方向中心軸線に実質的に平行な方
向に前記出力軸を並進させるようにして成る、請求項２
のトルク分配装置。3. The at least one torque transmitting ball is received in a first groove formed in the outer race and a second groove formed in the inner race, the at least one ball Torque transmitting balls cooperate with the first groove of the outer race and the second groove of the inner race to translate the output shaft in a direction substantially parallel to the longitudinal central axis. 2. The method according to claim 2, wherein
Torque distribution device. 【請求項４】 前記スプロット軸を貫いて大体において
縦方向に延びる少なくとも１つの通路を備え、前記伸縮
式定速度継手を潤滑する潤滑手段をさらに備えた、請求
項１のトルク分配装置。4. The torque distribution device of claim 1, further comprising at least one passage extending generally longitudinally through the splot shaft and further comprising lubricating means for lubricating the telescopic constant velocity joint. 【請求項５】 前記スプロット軸の従動端部の近くに配
置された第１の空洞に連通する第１の端部と、前記伸縮
式定速度継手内に位置させた第２の空洞に連通する第２
の端部とを、前記少なくとも１つの通路に設け、 この少なくとも１つの通路を、大体において円筒形に
し、前記第２空洞に、大体において円筒形の部分を設
け、前記少なくとも１つの通路と前記第２の空洞の前記
部分とがそれぞれ第１及び第２の直径を持つようにし、
これ等の第１及び第２の直径を相互に違わせて、前記ス
プロット軸が回転させられるときに、前記第２の空洞と
前記少なくとも１つの通路との間に圧力差を生ずること
により、潤滑流体を前記伸縮式定速度継手を潤滑するた
めに前記少なくとも１つの通路に流通させるようにして
成る、請求項４のトルク分配装置。5. A first end communicating with a first cavity located near the driven end of the sprout shaft and a second cavity located within the telescoping constant velocity joint. Second
And an end of the at least one passage, the at least one passage being generally cylindrical and the second cavity being provided with a generally cylindrical portion, the at least one passage and the first passage being The said portion of the two cavities having a first and a second diameter respectively,
Lubricating these first and second diameters from each other to create a pressure differential between the second cavity and the at least one passage when the splot shaft is rotated. The torque distributor of claim 4, wherein fluid is circulated through the at least one passage to lubricate the telescopic constant velocity joint. 【請求項６】 前記第２の直径を前記第１の直径より大
きくすることにより、前記圧力差によつて潤滑流体を前
記第１の空洞から前記少なくとも１つの通路を通つて前
記第２の空洞に流し、前記スプロケット軸が回転させら
れるときに、前記伸縮式定速度継手を潤滑するようにし
て成る、請求項５トルク分配装置。6. The second diameter is greater than the first diameter to allow lubricating fluid to flow from the first cavity through the at least one passage to the second cavity due to the pressure difference. 6. The torque distribution device according to claim 5, wherein the expansion type constant velocity joint is lubricated when the sprocket shaft is rotated. 【請求項７】 前記出力軸の直径を細くした部分に対し
包囲する関係に配置されこの出力軸の部分と一緒に回転
するように、この出力軸の部分にスプライン結合された
連結部材と、 前記ハウジングに取付けられ、前記連結部材に対して弾
性的に付勢された唇状シールから成り前記連結部材を前
記ハウジングに密封する密封手段と、をさらに備えた、
請求項４のトルク分配装置。7. A coupling member disposed in a surrounding relationship with the reduced diameter portion of the output shaft and splined to the output shaft portion for rotation therewith, A sealing means attached to the housing and comprising a lip seal elastically biased against the connecting member for sealing the connecting member in the housing;
The torque distribution device according to claim 4. 【請求項８】 前記密封手段にさらに、前記ハウジング
に取り付けられ、前記唇状シールの前方に前記連結部材
に対し囲む関係に延びる遮蔽を設けた、請求項７のトル
ク分配装置。8. The torque distribution device of claim 7, wherein said sealing means further comprises a shield attached to said housing and extending in front of said lip seal in a surrounding relationship with said connecting member. 【請求項９】 前記出力軸の前端部にねじ込んだナツト
を備え、前記出力軸に対する前記連結部材の軸線方向変
位を防ぐ防止手段をさらに備えた、請求項７のトルク分
配装置。9. The torque distribution device according to claim 7, further comprising a nut screwed into a front end portion of the output shaft, and further comprising a prevention unit for preventing axial displacement of the connecting member with respect to the output shaft. 【請求項１０】 前記出力軸が、第１の出力軸であり、 前記ハウジング内に回転可能に支えられた第２の出力軸
と、前記入力軸を前記第２の出力軸に駆動作用を生ずる
ように連結手段とをさらに備えた、請求項１のトルク分
配装置。10. The output shaft is a first output shaft, and a second output shaft rotatably supported in the housing and the input shaft generate a driving action on the second output shaft. The torque distribution device according to claim 1, further comprising a connecting means. 【請求項１１】 前記入力軸を、前記スプロケット軸に
駆動作用を生ずるように連結する前記連結手段に駆動チ
エーンを設け、 前記入力軸を前記第２の出力軸に駆動作用を生ずるよう
に連結する前記連結手段に遊星歯車セットを設けた、請
求項１０のトルク分配装置。11. A drive chain is provided in the connecting means for connecting the input shaft to the sprocket shaft so as to generate a driving action, and the input shaft is connected for generating a drive action to the second output shaft. The torque distribution device according to claim 10, wherein the connecting means is provided with a planetary gear set. 【請求項１２】 前記第１の出力軸を、前記第２の出力
軸から横方向に間隔を置きこの第２の出力軸に対して傾
斜させて成る、請求項１０のトルク分配装置。12. The torque distributor of claim 10, wherein the first output shaft is laterally spaced from the second output shaft and is inclined with respect to the second output shaft. 【請求項１３】 前記第１の出力軸が前部出力軸であ
り、 前記第２の出力軸が後部出力軸である、請求項１０のト
ルク分配装置。13. The torque distribution device of claim 10, wherein the first output shaft is a front output shaft and the second output shaft is a rear output shaft. 【請求項１４】 ハウジングと、 このハウジング内に回転可能に支えられた第１の軸と、 前記ハウジング内に回転可能に支えられた第２の軸と、 前記第１及び第２の軸の一方から、これ等の第１及び第
２の軸の他方にトルクを移送し、かつこれ等の第１及び
第２の軸の相対的な軸線方向変位を許容するように、前
記第１及び第２の軸に結合され、前記ハウジング内に入
れられた伸縮式定速度継手と、 この伸縮式定速度継手を潤滑流体で潤滑する潤滑手段
と、 前記潤滑流体を前記ハウジング内に保持するシールと、
を包含する駆動列サブアセンブリ。14. A housing, a first shaft rotatably supported in the housing, a second shaft rotatably supported in the housing, and one of the first and second shafts. From the first and second shafts to transfer torque to the other of the first and second shafts and to allow relative axial displacement of the first and second shafts. An expansion type constant velocity joint which is coupled to the shaft of the casing and is placed in the housing, a lubrication unit which lubricates the expansion type constant velocity joint with a lubricating fluid, and a seal which holds the lubricating fluid in the housing,
A drive train subassembly including. 【請求項１５】 前記伸縮式定速度継手が、二重オフセ
ット型伸縮式定速度継手である、請求項３のトルク分配
装置。15. The torque distribution device according to claim 3, wherein the expansion type constant velocity joint is a double offset type expansion type constant velocity joint.
JP19101295A 1994-07-05 1995-07-05 Torque divider and drive train sub assembly Pending JPH08169247A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US27116994A 1994-07-05 1994-07-05
US08/271169 1994-07-05

Publications (1)

Publication Number Publication Date
JPH08169247A true JPH08169247A (en) 1996-07-02

Family

ID=23034478

Family Applications (1)

Application Number Title Priority Date Filing Date
JP19101295A Pending JPH08169247A (en) 1994-07-05 1995-07-05 Torque divider and drive train sub assembly

Country Status (2)

Country Link
JP (1) JPH08169247A (en)
DE (1) DE19523313A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2674788C1 (en) * 2018-03-14 2018-12-13 Акционерное общество "Брянский автомобильный завод" Four-axle wheeled vehicle torque divider

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10305182A1 (en) * 2003-02-08 2004-08-19 Zf Friedrichshafen Ag Axial transfer box gearing for work machine is arranged with motor/gearing unit so as not to form a rigidly connected unit for a narrower construction
DE102004053121B4 (en) * 2004-11-03 2011-12-29 Iglhaut Gmbh Motor vehicle with four-wheel drive

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2674788C1 (en) * 2018-03-14 2018-12-13 Акционерное общество "Брянский автомобильный завод" Four-axle wheeled vehicle torque divider

Also Published As

Publication number Publication date
DE19523313A1 (en) 1996-01-11

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